Positive displacement pump system and method

ABSTRACT

Systems and methods including a motor or electromagnets to control the movement of one or more pistons in a pumping chamber. The pumping chamber may include a pump inlet and a pump outlet in fluid communication with the pumping chamber. Surfaces on a piston or pumping chamber may include hydrodynamic bearing surfaces.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority to U.S. Provisional Patent ApplicationNo. 60/806,667 filed on Jul. 6, 2006, the disclosure of which is hereinincorporated by reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

Embodiments of the present invention generally relate to pumps. Morespecifically, and not by way of limitation, embodiments of the presentinvention relate to positive displacement pumps for the circulation offluids.

2. Description of Related Art

Many natural and manmade fluids contain molecules that can be damaged ordestroyed by excessive shearing strains or stagnation that can occur indevices that attempt to pump these fluids. Fluids containing moleculeswith high molecular weights such as proteins, long stranded syntheticpolymers, DNA, RNA, or fluids such as blood, which containconcentrations of delicate cells, are especially susceptible to beingcompromised by many conventional pumping techniques.

Typical axial flow and centrifugal pumps operate by rotating an impellerat very high speeds, often exceeding 12,000 RPM. The shearing stressesthat can arise at these velocities can strain larger fluid moleculesuntil they break, leading to destruction or undesirable alteration ofthe pumping medium. For instance, it is well documented that the pumpingof blood using centrifugal and axial flow pumps shears the phospholipidbilayer of erythrocytes and platelets to the point of lysing the cellsand releasing their cytosolic proteins and organelles into the bloodstream. This phenomenon, known as hemolysis, is an issue in the field ofartificial blood circulation because the releasing of hemoglobin intothe blood stream can cause kidney failure in patients who receive thisblood. Thus, there is useful need for pump designs that can providefluid circulation without damaging a delicate pumping medium such asblood.

Further objects and advantages of this system and method will becomeapparent from a consideration of the drawings and ensuing description.

SUMMARY OF THE INVENTION

Embodiments of the present disclosure provide systems and methods forpumping fluids. While certain embodiments may be particularly suited forpumping delicate fluids with low shearing strains, it is understood thatembodiments of the present disclosure are not limited to pumping suchfluids. Other embodiments may be used to pump fluids that are notdelicate or do not have low shearing strains.

Certain embodiments comprise: a pumping chamber forming a loop; a pumpinlet in fluid communication with the pumping chamber; a pump outlet influid communication with the pumping chamber; a first piston disposedwithin the pumping chamber; a second piston disposed within the pumpingchamber; an electric motor; and an electromagnet, wherein the system isconfigured such that during operation: the electromagnet is initiallycoupled to the first piston; the electric motor is initially coupled tothe second piston; the electromagnet is subsequently coupled to thesecond piston; and the electric motor is subsequently coupled to thefirst piston. In certain embodiments, the electromagnet is coupled toeither the first or second piston when the electromagnet is energizedand the electromagnet is not coupled to either the first or secondpiston when the electromagnet is de-energized. Certain embodimentsfurther comprise a magnetic ring, and are configured such that duringoperation: the electric motor exerts a first magnetic force on the firstpiston; the magnetic ring exerts a second magnetic force on the firstpiston; and the first magnetic force opposes the second magnetic force.In certain embodiments, the magnetic ring and/or the pistons comprise apermanent magnet or Halbach array. In certain embodiments, the system isconfigured such that during operation: the motor comprises a rotor witha magnetic link (which may comprise a permanent magnet or Halbach array)and the magnetic link is initially coupled to the second piston andsubsequently coupled to the first piston.

Certain embodiments are configured such that during operation a portionof the magnetic link extends beyond a leading face of the piston. Incertain embodiments, the system is configured such that during operationthe pump inlet is inserted into a ventricle and the pump outlet is influid communication with the ascending aorta, the descending aorta, or apulmonary artery. In certain embodiments, the system is configured suchthat: the motor comprises a rotor coupled to a linking arm; the linkingarm is coupled to a first magnet, wherein the first magnet is located ona first side of the piston during operation; the linking arm is coupledto a second magnet, wherein the second magnet is located on a secondside of the piston during operation; and the first side is opposed tothe second side. In certain embodiments, the first piston or the secondpiston comprise a hydrodynamic bearing surface.

Other embodiments comprise a method of pumping a fluid, the methodcomprising: providing a pumping chamber, wherein the pumping chambercontains the fluid; providing a pump inlet in fluid communication withthe pumping chamber; providing a pump outlet in fluid communication withthe pumping chamber; providing a first piston disposed within thepumping chamber; providing a second piston disposed within the pumpingchamber; providing an electric motor comprising a rotor; providing anelectromagnet; coupling the electromagnet to the first piston; couplingthe rotor to the second piston; holding the first piston in a firstlocation with the electromagnet; rotating the rotor and moving thesecond piston closer to the first piston so that a portion of the fluidis forced out of the pump outlet; de-energizing the electromagnet anduncoupling the electromagnet from the first piston; energizing theelectromagnet so that it couples to the second piston; and coupling therotor to the first piston. Certain embodiments further comprise rotatingthe rotor and moving the first piston closer to the second piston sothat a portion of the fluid is forced out of the pump outlet. In certainembodiments, the first location is between the pump inlet and the pumpoutlet.

Still other embodiments comprise: a pumping chamber comprising an innersurface forming a loop; a pump inlet in fluid communication with thepumping chamber; a pump outlet in fluid communication with the pumpingchamber; a piston disposed within the pumping chamber; and a firstelectric motor magnetically coupled to the piston, wherein: the pistoncomprises a hydrodynamic bearing surface configured to repel the pistonaway from the inner surface as the piston moves within the pumpingchamber. In certain embodiments, the loop is centered about a centralaxis; the piston comprises an upper surface, a lower surface, an innersurface, an outer surface, a leading face, and a trailing face; and theinner surface comprises an upper wall, a lower wall, an inner wall andan outer wall.

In certain embodiments, during operation: a first lower gap existsbetween the lower surface and the lower wall proximal to the leadingface; a second lower gap exists between the lower surface and the lowerwall proximal to the trailing face; the first lower gap is larger thanthe second lower gap; a first upper gap exists between the upper surfaceand the upper wall proximal to the leading face; a second upper gapexists between the upper surface and the upper wall proximal to thetrailing face; and the first upper gap is larger than the second uppergap. In certain embodiments, a portion of the lower surface is notperpendicular to the central axis and a portion of the upper surface isnot perpendicular to the central axis.

In certain embodiments, a first outer gap exists between the outersurface and the outer wall proximal to the leading face; a second outergap exists between the outer surface and the outer wall proximal to thetrailing face; and the first outer gap is larger than the second outergap. Certain embodiments comprise a pinch valve between the pump inletand the pump outlet. Certain embodiments also comprise a second pistondisposed within the pumping chamber, and a second electric motor coupledto the second piston, wherein the second piston comprises a hydrodynamicbearing surface configured to repel the second piston away from theinner surface as the second piston moves within the pumping chamber.

Certain embodiments comprise: a power supply; a driver circuitelectrically coupled to the electric motor and the power supply; amicroprocessor electrically coupled to the driver circuit; and a sensorfor sensing a position of the piston within the pumping chamber,wherein: the driver circuit is configured to selectively couple thepower supply to the electric motor upon receiving a control signal; thesensor is electrically connected to the microprocessor; themicroprocessor is configured to interpret the position from the sensor;the microprocessor is configured to output the control signal to thedriver circuit. In certain embodiments, a position and a velocity of thepiston are controlled to produce a predetermined waveform in an outletflow from the pump outlet. Certain embodiments comprise a fluid withinthe pumping chamber and a sensor configured to measure a property of thefluid. In certain embodiments, the piston or inner surface comprise oneor more of the following: a nanoparticulate surface, a microporouscoating, or a fibrous flocking. In certain embodiments thenanoparticulate surface, microporous coating, or fibrous flocking areconfigured to facilitate endothelial or pseudoneointimal protein or cellaggregation.

Certain embodiments comprise a pacemaker and a microprocessor, wherein:the pacemaker comprises one or more electrodes electrically coupled to aheart; the pacemaker is electrically coupled to the microprocessor; thepacemaker provides a depolarization output to the one or moreelectrodes; and the heart is controlled to contract at a predeterminedtime relative to an actuation stroke of the pump. Certain embodimentscomprise a sensor, wherein the sensor is configured to sense aphysiological parameter and the system is configured to increase ordecrease a volumetric flow rate from the pumping chamber based on thephysiological parameter. In certain embodiments the sensor comprises oneor more electrodes for measuring thoracic impedance, p-wave activity,renal sympathetic nerve activity, or aortic nerve activity. In otherembodiments, the sensor comprises an accelerometer for sensing heartcontraction, diaphragm motion, bodily inclination, or walking pace.

Certain embodiments comprise a pump for circulating fluid comprising: apumping chamber; a pump inlet in fluid communication with the pumpingchamber; a pump outlet in fluid communication with the pumping chamber;a drive piston disposed within the pumping chamber; and a hollow valvesleeve configured to recess into the pump outlet.

Other embodiments comprise: a pumping chamber forming a loop; a pumpinlet in fluid communication with the pumping chamber; a pump outlet influid communication with the pumping chamber; a piston disposed withinthe pumping chamber; an electric motor comprising a rotor coupled to ashaft; a magnet coupled to an end of the shaft; a sensor proximal to themagnet; and a control system, wherein: the electric motor ismagnetically coupled to the piston; the magnet produces a magneticvector that rotates with the rotor; the sensor is configured sense themagnetic vector; and the control system is configured to determine theangular position of the rotor. In certain embodiments, the sensor is a2-axis Hall effect sensor and the electric motor is an axial flux motor.In certain embodiments, the control system is configured to access alookup table.

Certain embodiments comprise a pumping chamber comprising an innersurface forming a loop; a pump inlet in fluid communication with thepumping chamber; a pump outlet in fluid communication with the pumpingchamber; a first piston disposed within the pumping chamber; and aseries of electromagnets disposed around the pumping chamber, wherein:the series of electromagnets are configured to move the first pistonaround the pumping chamber; and the first piston comprises ahydrodynamic bearing surface configured to repel the first piston awayfrom the inner surface as the first piston moves within the pumpingchamber. Certain embodiments further comprise a second piston disposedwithin the pumping chamber, wherein: the series of electromagnets areconfigured to move the second piston around the pumping chamber; and thesecond piston comprises a hydrodynamic bearing surface configured torepel the second piston away from the inner surface as the second pistonmoves within the pumping chamber. Certain embodiments further comprise apinch valve between the pump inlet and pump outlet.

As used herein, the terms “a” and “an” are defined as one or more unlessthis disclosure explicitly requires otherwise.

The term “substantially” and its variations are defined as being largelybut not necessarily wholly what is specified as understood by one ofordinary skill in the art, and in one non-limiting embodiment the term“substantially” refers to ranges within 10%, preferably within 5%, morepreferably within 1%, and most preferably within 0.5% of what isspecified.

The terms “comprise” (and any form of comprise, such as “comprises” and“comprising”), “have” (and any form of have, such as “has” and“having”), “include” (and any form of include, such as “includes” and“including”) and “contain” (and any form of contain, such as “contains”and “containing”) are open-ended linking verbs. As a result, a method ordevice that “comprises,” “has,” “includes” or “contains” one or moresteps or elements possesses those one or more steps or elements, but isnot limited to possessing only those one or more elements. Likewise, astep of a method or an element of a device that “comprises,” “has,”“includes” or “contains” one or more features possesses those one ormore features, but is not limited to possessing only those one or morefeatures. Furthermore, a device or structure that is configured in acertain way is configured in at least that way, but may also beconfigured in ways that are not listed.

The term “coupled,” as used herein, is defined as connected, althoughnot necessarily directly, and not necessarily mechanically.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of one embodiment of the presentdisclosure.

FIG. 2 is a section view of the embodiment of FIG. 1.

FIG. 3 is a side view of one embodiment of the present disclosure.

FIG. 4 is a side view of one embodiment of the present disclosure.

FIG. 5 is a schematic of a control system used in certain embodiments ofthe present disclosure.

FIG. 6 is a schematic of a driver circuit diagram used in certainembodiments of the present disclosure.

FIG. 7 is a section view of one embodiment of the present disclosureduring operation.

FIG. 8 is a section view of one embodiment of the present disclosureduring operation.

FIG. 9 is a section view of one embodiment of the present disclosureduring operation.

FIG. 10 is a section view of one embodiment of the present disclosureduring operation.

FIG. 11 is a section view of one embodiment of the present disclosureduring operation.

FIG. 12 is a section view of one embodiment of the present disclosureduring operation.

FIG. 13 is a section view of one embodiment of the present disclosureduring operation.

FIG. 13A is a perspective view of magnetic shielding clips used incertain embodiments of the present disclosure.

FIG. 13B is a perspective view of a magnetic shielding clip used incertain embodiments of the present disclosure.

FIG. 14 is a side view of one embodiment of the present disclosure.

FIG. 15 is a section view of the embodiment of FIG. 14.

FIG. 16 is a perspective view of one embodiment of the presentdisclosure.

FIG. 17 is an exploded view of the embodiment of FIG. 16.

FIG. 18 is an exploded view of one embodiment of the present disclosure.

FIG. 19 is a section view of one embodiment of the present disclosure.

FIG. 20 is a section view of the embodiment of FIG. 19.

FIG. 21 is a section view of one embodiment of the present disclosure.

FIG. 22 is a section view of the embodiment of FIG. 21.

FIG. 23 is a side view of the embodiment of FIG. 21.

FIG. 24 is a section view of one embodiment of the present disclosure.

FIG. 25 is a section view of the embodiment of FIG. 25.

FIG. 26 is a view of one embodiment of the present disclosure inoperation.

FIG. 27 is a section view of one embodiment of the present disclosure.

FIG. 28 is a section view of the embodiment of FIG. 28.

FIG. 29 is a section view of one embodiment of the present disclosure.

FIG. 30 is a section view of the embodiment of FIG. 29.

FIG. 31 is perspective view of a piston in one embodiment of the presentdisclosure.

FIG. 32 is a section view of a component of one embodiment of thepresent disclosure.

FIG. 33 is a section view of multiple embodiments of the presentdisclosure.

FIGS. 34A-34D are section views of an embodiment of the presentdisclosure in different stages of operation.

FIG. 35 is a schematic of an embodiment of the present disclosure.

FIG. 36 is a partial side section view of an embodiment of the presentdisclosure.

FIG. 37 is a partial end section view of the embodiment of FIG. 36.

FIG. 38 is a partial top section view of the embodiment of FIG. 36.

FIG. 39 is a partial end view of an embodiment of the presentdisclosure.

FIG. 40 is a partial end view of an embodiment of the presentdisclosure.

FIG. 41 is a partial end view of an embodiment of the presentdisclosure.

FIG. 42A is a partial end view of an embodiment of the presentdisclosure.

FIG. 42B is a partial side view of different embodiments of the presentdisclosure.

FIG. 42C is a partial top view of an embodiment of the presentdisclosure.

FIG. 43 is an exploded view of an embodiment of the present disclosure.

FIG. 44 is an assembled view of a portion of an embodiment of thepresent disclosure.

FIG. 45 is a side view of a portion of an embodiment of the presentdisclosure.

FIG. 46 is a perspective view of a portion of an embodiment of thepresent disclosure.

FIG. 47 is a side view of a portion of an embodiment of the presentdisclosure.

FIG. 48 is a flowchart of a control system used for an embodiment of thepresent disclosure.

FIG. 49 is an exploded view of an embodiment of the present disclosure.

FIG. 50 is a section view of the embodiment of FIG. 49.

FIG. 51 is a perspective view of a portion of an embodiment of thepresent disclosure.

FIGS. 52-56 are section views of a portion of an embodiment of thepresent disclosure.

FIGS. 57-62 are section views of a portion of an embodiment of thepresent disclosure.

FIG. 63 is a perspective view of a portion of an embodiment of thepresent disclosure.

FIG. 64 is a perspective view of an embodiment of the presentdisclosure.

FIGS. 65-66 are views of an embodiment of the present disclosureinserted in a patient.

FIG. 67 is an exploded view of an embodiment of the present disclosure.

FIG. 68 is a side view of a portion of an embodiment of the presentdisclosure.

FIG. 69 is a top view of the embodiment of FIG. 67.

DETAILED DESCRIPTION OF THE INVENTION

FIGS. 1 and 2 show a perspective and sectioned view, respectively, of apump 100 with an inlet 110 and an outlet 120. It should be appreciatedthat pump 100 shown in FIGS. 1 and 2 is one exemplary embodiment, andthe present invention should not be limited to the embodiment shown. Thesame is true for all other Figures, which are provided as examples only.

The embodiments illustrated in FIGS. 1-13 show a pumping chamber 130forming a loop or ring comprised of an inner wall 140 and an outer wall150 defining a lumen generated by the revolution of a two-dimensionalenclosed contour, in this case a circle, about a coplanar axis lyingoutside the contour. It should be appreciated that many two dimensionalenclosed contours can be used to define the lumen including a square,ellipse, polygon, conic, etc. It should also be appreciated that therevolution path should not be restricted to a circle. For instance, theenclosed contour may be swept around an oval, ellipse, etc. Pumpingchamber 130 is comprised of a rigid plastic material such as poly etherether ketone (PEEK) blow molded or injection molded into shape. However,pumping chamber 130 can consist of a variety of materials includingplastic, titanium, stainless steel, aluminum, or a photo-reactivepolymeric resin used in stereolithography. Pumping chamber 130 containsa first orifice 115 and second orifice 125 located along its outerperimeter sized so that a pair of pistons 160 and 170 residing withinpumping chamber 130 cannot enter the orifices or catch along theinterface where the orifice 115 meets inlet 110 or orifice 125 meetsoutlet 120. Inlet 110 is in fluid communication with first orifice 115of pumping chamber 130 such that inlet 110 joins pumping chamber 130 atan angle 180. Outlet 120 is in fluid communication with second orifice125 of pumping chamber 130 such that outlet 120 joins pumping chamber130 at an angle 190. It should be appreciated that the position of firstorifice 115 and second orifice 125 are not required to reside along theradial perimeter of pumping chamber 130, but could exist in variouspositions elsewhere on pumping chamber 130. It should also beappreciated that inlet 120 and outlet 130 could intercept the pumpingchamber at a variety of angles. It should further be appreciated thatthe outer wall of the pumping chamber need not be an identically shapedoffset of the inner wall of the pumping chamber. Where inner wall 140has a direct relationship to the volume created by the revolution of thetwo-dimensional enclosed contour, outer wall 150 of pumping chamber 130can adopt many different shapes to accommodate the need for mountingsensors, electromagnets, wires, etc. In the embodiment shown, pumpingchamber 130 is composed of two halves 132 and 134, which separate andattach along a plane 200. Between and nearest the inflow and outflowconduits 110 and 120, a flange 135 exists on each half 132, 134 ofpumping chamber 130. Flange 135 comprises counter-bored clearance holes137 in which fasteners 138 are inserted and tightened down to create ahermetic seal. No flange exists along the second attachment surface 139to allow for a plurality of solenoids 145 to be slid onto each half 132,134 of pumping chamber 130. The attachment of each half 132, 134 atsecond attachment surface 139 is sealed by ultrasonic welding of thecontact seam. It should be appreciated that many materials and methodsmay be used to attach the chamber halves 132, 134 together includingadhesives, snap fits, press fits, fasteners, ultrasonic welding, laserwelding, etc. In certain embodiments, inner wall 140 of pumping chamber130 is coated with a hydrophilic lining (not shown) that partiallyabsorbs fluid to enhance lubricity. The inner lining of pumping chamber130 and/or the pistons 160, 170 may be coated in the following materialtypes for the facilitation of protein or cellular aggregation forincreasing lubricity, sealing, durability, and lowering hemolysis andthrombosis: a nano-particulate surface (carbon, silicate, or titaniumbased), a micro-porous ceramic, or a fibrous flocking material. Itshould be appreciated that many other surface coatings, such asdiamond-like carbon and titanium nitride, may be used to provideincreases in biocompatibility, lubricity, sealing, and durability, anddecreases in thrombosis and hemolysis, and that these materials serveonly as an example of several embodiments.

The present embodiment further shows two pistons 160, 170 residingwithin the lumen of pumping chamber 130. Each piston 160, 170 contains arare earth magnetic sphere 161, 171 encapsulated by two halves 162, 172of a rigid housing that joins and seals along an edge with epoxy 9 (notshown). The magnetic spheres 161, 171 are fixed at the center of pistons160, 170 with epoxy so that the spheres 161, 171 cannot rotate withinpistons 160, 170. The housing of each piston 160, 170 conforms to agreat extent with the inner shape of the lumen or pumping chamber 130,the pistons 160, 170 having a toroidal curvature terminating on bothends with a planar face. In the embodiment shown, the two planar endfaces of pistons 160, 170 are configured so that the end faces areparallel. However, it should be appreciated that many different pistonshapes could be used including pistons whose end faces are angled andpistons with sculpted extensions to facilitate the smooth transition offluid into and out of the pump. In certain embodiments, all edges alongthe piston are filleted to minimize frictional wear and a hydrophiliccoating (not shown) that partially absorbs fluid surrounds each piston160, 170, enhancing its lubricity. While residing in pumping chamber130, small clearance gaps 163 and 167 exist between piston 160 andpumping chamber 130 allowing piston 160 to move within pumping chamber130 without significant contact friction. Similarly, small clearancegaps 173 and 177 exist between the piston 170 and pumping chamber 130.The orientation of spherical magnet 161, 171 within each piston 160, 170are set such that the net magnetic vector points substantially parallelto the instantaneous velocity vector of the piston as it moves in thepumping chamber 130. Pistons 160, 170 are placed within pumping chamber130 at orientations such that pistons 160, 170 magnetically oppose oneanother as they reside within pumping chamber 130. Pistons 160, 170 arealso sized to prevent their insertion or collision with orifices 115,125 of pumping chamber 130.

FIGS. 1-13 further show one embodiment of a means for actuating pistons160, 170 within pumping chamber 130. In the embodiments shown, aplurality of solenoids 145 are discretely placed along outer wall 150 ofpumping chamber, each solenoid 145 consisting of a wound conductorsupported by a resin to retain a self standing ring shape that extendsaround pumping chamber 130. Each solenoid 145 is slid onto pumpingchamber 130 and mounted into place using an adhesive (not shown). Itshould be appreciated that the conducting wire of each solenoid 145 canbe chosen from a wide variety of metals such as copper, aluminum, gold,silver, Litz wire, etc and the gauge of the wire can be varied. Eachsolenoid 145 conforms along its inner surface with the curvature of theouter wall 150 of pumping chamber 130. Each solenoid 145 is also taperedso that the thickness (shown as dimension “T” in FIG. 2) of the solenoiddecreases as one moves radially inward from the outer edge of pump 100towards the center, facilitating a maximal packing factor of coils ontopumping chamber 130. In the embodiments shown, solenoids 145 take theaspect ratio approximating a Brook's coil so as to maximize the forcetransduced between each piston 160, 170 and each solenoid 145. It shouldbe appreciated that in other embodiments, more or less solenoids couldbe used and that the solenoids can be of a wide range of shapes and eachneed not be of identical shape.

FIG. 3 shows one embodiment of a means for sensing the angular positionsof the magnetic pistons 160, 170 using a 2-axis Hall effect sensor 155located in the void at the center of the pump. Sensor 155 can be mountedon a variety of support structures (not shown) extending from outer wall150 of pumping chamber 130 into void 156 at the center of pump 100. Forpurposes of clarity, solenoids 145 or other means for actuating pistons160, 170 are not shown in FIG. 3.

FIG. 4 shows another embodiment of a means for sensing the angularpositions of the magnetic pistons 160, 170 using a plurality of singleaxis Hall effect sensors 157 positioned around the perimeter of outerwall 150 of pumping chamber 130 and mounted with an adhesive (not shown)or other suitable means. For purposes of clarity, solenoids 145 or othermeans for actuating pistons 160, 170 are not shown in FIG. 4.

As shown in FIG. 5, one embodiment of a control system 111 for operatingpump 100 comprises a power supply 101, a microprocessor 102, a drivercircuit 103, a plurality of solenoids or electromagnets 104, and aplurality of sensors 105. It should be appreciated that microprocessor102 could take the form of a real time operating system,microcontroller, CPU, etc. Microprocessor 102 is electrically connectedto a driver circuit 103 and sensors 105 located on pump 100. Drivercircuit 103 is electrically connected to power supply 101 andelectrically connected to solenoids or electromagnets 104 (or othermeans for actuating pistons 160, 170 within pumping chamber 130). Itshould be appreciated that power supply 101 can comprise a bench topalternating or direct voltage source, a battery, a fuel cell, a bank ofcapacitors, etc.

As shown in FIG. 6 one embodiment of driver circuit 101 comprises a fullbridge MOSFET driver 133 with pullup capacitors 116 and 117 and flybackdiodes 114.

In the embodiment shown, pump 100 circulates fluid (not shown) in twophases, a drive phase and a transition phase, which are cyclicallyalternated in the operation of pump 100. FIG. 7 shows piston 160 in afirst position with piston 170 located substantially between inlet 110and outlet 120 and the piston 160 residing close to piston 170 nearinlet 110. This position marks the end of the transition phase and thebeginning of the drive phase. In the embodiment shown, one cycle of thedrive phase occurs by actuating piston 160 in a clockwise motion aroundthe lumen of pumping chamber 130 while maintaining piston 170 in theposition between inlet 110 and outlet 120. Piston 160 is actuatedclockwise in the embodiment shown by delivering a current to solenoid145 b in a direction which produces an attractive force on the piston160. It should be appreciated that the solenoids 145 c and 145 d mayalso be energized to produce additional attractive forces on the piston160 as well, as is the case when needing a higher force to pump fluidagainst a higher pressure at outlet 120. It should also be appreciatedthat the solenoid 145 a may be energized to produce a repelling force tofurther accelerate piston 160 in a clockwise direction. However, in theembodiment shown, first solenoid 145 a remains off in this initialsequence to prevent producing an attractive force on the piston 170.Piston 170 is located close to solenoid 145 a and therefore could moveif solenoid 145 a were energized to repel piston 160. The forces placedon piston 160 by the solenoid 145 b cause it to move clockwise. Aspiston 160 begins to move, it pushes on the fluid that resides in thevolume between its leading face and outlet 120. Due to the closeclearance between the inner wall 140 and piston 160, which is enhancedby the hydrophilic coating that further facilitates a sealing effect,the fluid does not substantially leak around piston 160, but is ratherforced to move with piston 160. Simultaneously, the solenoid 145 m isdelivered current by control system 111 (schematically shown in FIG. 5)to produce a holding force which isolates piston 170 in the positionbetween inlet 110 and outlet 120. Piston 170, due to its geometry andhydrophilic coating, also produces a substantial occlusion to the fluidflow. It is in this fashion that the piston 160 pressurizes fluidbetween its leading face and piston 170, causing the fluid to exitpumping chamber 130 through outlet 120. Simultaneously, the expandingvolume change induced by the motion piston 160 creates a lower pressurebetween its lagging face and piston 170. This low pressure forces fluidto enter into pumping chamber 130 through inlet 110. As piston 160 movesclockwise, the solenoids it approaches are delivered currents by controlsystem 111 to further attract piston 160 and the solenoids that piston160 has recently passed through are delivered reversed currents bycontrol system 111 to further repel piston 160. As piston 160 crossesthe midplane of each solenoid, control system 111 reverses the directionof the current supplied to that particular solenoid in order to producea repelling force which expels piston 160 through the solenoid along thesame clockwise direction. The use of solenoids to produce both anattracting force and a repelling force provides greater efficacy in thetransportation of piston 160, and surpasses the performance of the priorart designs which only utilize attractive forces to propel the pistonaround the pumping chamber.

FIGS. 8-13 show the progression of piston 160 around pumping chamber 130during operation of pump 100. FIGS. 8-10 show the completion of thedrive phase of the pump operation, in which piston 160 forces fluid toexit through outlet 120 and enter through inlet 110. FIGS. 11 and 12show the transition phase of pump operation, in which piston 160 andpiston 170 effectively switch functions. During this phase, piston 160is transitioning from the “drive” piston to the “stationary” piston.Similarly, piston 170 is no longer stationary and is now beingpositioned for use as the drive piston. In FIG. 13, pump 100 hascompleted one cycle of operation and is ready to begin a second cycle,using piston 170 as the drive piston and piston 160 as the stationarypiston. Pump 100 repeats the cycle described above during continuedoperation.

Referring back now to FIGS. 3-5, control system 111 uses knowledge ofthe instantaneous position of pistons 160, 170 and the absolute positionof the coils (not shown) to make the decision of when to turn eachsolenoid 145 on and off and which direction to send the current whileeach solenoid 145 is on. The position of pistons 160, 170 is sensed by asingle 2-axis Hall effect sensor 155 or a series of single axis Halleffect sensors 157 mounted around pumping chamber 130. Sensors 155, 157sense the magnitude and direction of the magnetic field and relay thisinformation as a voltage level to microprocessor 102 which translatesthis data through a conversion algorithm into the angular positions ofpistons 160, 170. Following a programmed algorithm, microprocessor 102then outputs an array of digital signals to a plurality of drivercircuits 103. In a preferred embodiment, each driver circuit 103 iscomprised of a full-bridge configuration of MOSFETs connected to asingle solenoid and a power supply. This full-bridge MOSFETconfiguration can be found prefabricated on an integrated circuit chipsuch as the L298 produced by ST electronics. Upon receiving theappropriate digital signal from microprocessor 102, driver circuit 103places the voltage of power supply 101 in a forward or reverse biasdirection across the terminals of a solenoid 145. Driver circuit 103 canalso remove the voltage from the terminals of the solenoid 145 whenmicroprocessor 102 directs the solenoid 145 to be turned off.Microprocessor 102 can send either TTL or pulse width modulated signalsto driver circuit 103 to control the direction and magnitude of thecurrent delivered to the solenoid 145. It should be appreciated that thelevel of current that is delivered to the solenoid 145 can be used tocontrol the drive piston at variable speeds. Flyback diodes are used toprevent current spikes from damaging the MOSFET chip due to the highinductance of the solenoid 145.

Referring additionally to FIGS. 7-12, while piston 160 is being drivenaround pumping chamber 130, piston 170 is held in place by attractiveand repulsive forces created by solenoids 145 a and 145 m. The directionand magnitude of the currents delivered to solenoids 145 a and 145 m iscontrolled by control system 111 such that the forces the piston 170experiences from pressure differences across its two faces are canceledby the solenoid forces, resulting in a zero net force on the 170 piston,which makes it remain stationary. A simple feedback loop is used in themicroprocessor 102 to deliver the correct currents to keep it held inplace. For instance, this can be accomplished in some cases by repellingthe piston 170 with both solenoids 145 a and 145 m, effectively trappingpiston 170 in position.

Solenoids 145 b through 145L drive the piston 160 in a clockwiserotation around pumping chamber 130 while the piston 170 is held inplace. In this fashion, the bolus of fluid that originally existedbetween the leading face of the piston 160 and the trailing face of thepiston 170 is effectively ejected from the pump through outlet 120.Likewise, a fresh bolus of fluid enters the lumen through inlet 110 bymeans of a vacuum force that arises by the expanding volume generatedbetween the lagging face of the piston 160 and the leading face ofpiston 170. In this fashion, piston 170 is isolated and acts as anisolation member or a virtual “valve” in the sense that it preventsfluid from flowing from the high pressure side to the low pressure sideof pumping chamber 130. It should be appreciated that the angle of thepiston faces and the angle and shape of inlet 110 and outlet 120 aredesigned to provide a smooth transition of the fluid into and out ofpump 100 without causing turbulence, eddies, stagnation points, orshearing stresses sufficient to damage delicate fluid particles.

As the piston 160 nears the end of the drive stroke it comes into closecontact with the piston 170. At this point the drive phase has ended andthe transition phase begins. During the transition phase piston 160 andpiston 170 move together in a clockwise direction until the piston 160resides in the isolation position where the piston 170 previouslyresided, located substantially between inlet 110 and outlet 120 and thepiston 170 resides in the position to begin the drive phase. Controlsystem 111 can achieve this synchronized jog of both pistons 160, 170 inone embodiment by controlling solenoid 145 a to attract the secondpiston and directing solenoid 145 m to repel the first piston. Oncepistons 160, 170 have completed this transition phase piston 170 is nowin position to execute the drive stroke of the drive stage and piston160 is positioned to be isolated between inlet 110 and outlet 120 toprovide proper occlusion. It is in this way that each piston alternatesbeing the driven piston and the isolated or stationary piston. The speedat which each of these cycles is performed, controlled by the magnitudeof currents delivered to solenoids 145 a-145 m, dictates the flow rateof pumping. It is important to note that this is a positive displacementpump in the sense that the displacement of the drive piston isproportional to the displacement of fluid that enters and leaves thepumping chamber. In this way the pump is largely capable of deliveringpulsatile outputs by ejecting discrete boluses of fluid.

In the embodiment shown, the movement of fluid was from inlet 110 tooutlet 120 through the clockwise actuations of drive piston 160.However, it should be appreciated that the pumping direction is easilyreversed by actuating the pistons in a counterclockwise fashion andperforming a similar set of steps.

Referring now to FIG. 13A, a plurality of magnetically permeableshrouding clips 144 are shown arranged in a circle. In certainembodiments, shrouding clips 144 are positioned around solenoids 145(shown in FIGS. 1 and 2) for increasing and ducting magnetic fluxtowards pistons 160 and 170, resulting in improved force transductionand higher efficiencies. As shown in FIG. 13A, discrete spacing ofshrouding clips 144 provides air gaps for the prevention of eddy currentgeneration. FIG. 13B illustrates a detailed view of a shrouding clip144.

FIGS. 14-15 show an additional embodiment comprising an alternativemeans for actuating and holding the pistons within the pumping chamber.In this embodiment, a pump 200 comprises an inlet 210, an outlet 220, apair of pistons 260, 270 and a pumping chamber 230 with an inner wall240 and an outer wall 250. Pump 200 further comprises a pair of DCpancake torque motors 245, 246 located in the void at the center ofpumping chamber 230. It should be appreciated that a variety of motortypes could be used including alternating current motors, direct currentmotors, stepper motors, induction motors etc. Each motor 245, 246 has acylindrical shape. Electric motor 245 is positioned above the electricmotor 246 such that the two motors share a common plane. Each electricmotor 245, 246 has a rotor (not shown) and an arm extending from therotor towards outer wall 250 of pumping chamber 230. A first arm 247 isconnected to the first rotor through a press fit on the shaft of therotor and a hole on arm 247. The distal end of arm 247 takes the shapeof crescent so that arm 247 wraps around a portion of outer wall 250 ofpumping chamber 230 leaving space so as not to interfere with inlet 210and outlet 220 of pumping chamber 230. The distal end of arm 247 iscomprised either wholly or partially of a magnetic material so that amagnetic force is transferred between the distal portion of arm 247 andmagnetic piston 260 residing within the lumen of pumping chamber 230.Second arm 248 is similarly connected to the second rotor (not shown) ofsecond motor 246 and coupled magnetically to second piston 270. Howevermotor 246 is oriented such that arm 248 is located on the opposite sideof pump 200 from first arm 247 so that each arm 247, 248 does notinterfere with the other.

In the embodiment shown in FIGS. 14-15, arms 247, 248 magneticallycouple to pistons 260, 270, respectively, within the lumen of pumpingchamber 230 with sufficient magnetic force such that an angulardisplacement of each arm 247, 248 moves its coupled piston by the sameangular amount. In this way, each motor 245, 246 is able to control theprecise location and motion of the internal pistons 260, 270 through therotation of each arm 247, 248. Pumping of fluid is achieved with thesimilar piston motion as described in the solenoid actuated pistonembodiment. In order to achieve this piston motion, each motor iscontrolled by a control circuit (not shown) similar to that previouslydescribed to either rotate its coupled piston or to hold it stationary.The microcontroller thus controls arms 247, 248 to perform the motiondescribed previously to achieve the expulsion of fluid from the lumenthrough outlet 220 and the refilling of the lumen through inlet 110.

Referring now to FIGS. 16-17 another embodiment comprises a pump 300with a pair of electric motors 345, 385 having a different configurationthan motor 245, 246 of FIGS. 14-15. In this embodiment, electric motors345, 385 are not located within the void at the center of the pumpingchamber 330, but instead are adjacent to pumping chamber 330. Electricmotor 345 comprises a coil core plate 346, coils 347, magnets, 348, anda magnet core plate 349. Similarly, electric motor 385 comprises a coilcore plate 386, coils 387, magnets 388, and a magnet core plate 389.Linkage 350 couples either electric motor 345 or 385 with magneticpiston 360. For purposes of clarity, FIGS. 16-17 show only one piston360; however, an additional piston can be incorporated in thisembodiment so that one piston acts as a driving piston and the otherpiston acts as a stationary piston. The operation of this embodiment issimilar to that of previously-described embodiments.

FIG. 18 shows yet another embodiment comprising a pump 400 with apumping chamber 430, a motor 445 and a pair of pistons (not shown). Inthis embodiment, motor 445 comprises a first magnet core plate 446 witha first linking arm 447, a first plurality of magnets 448, a first coil449, a first coil core plate 450, a second coil plate 451, a second coil452, a second plurality of magnets 453, and a second magnet core plate454 with a second linking arm 455. Motor 445 further comprises a shaft456, a first bearing 457 and a second bearing 458. Although motor 445 isconfigured differently than the motors described in the discussion ofprevious embodiments, the embodiment of FIG. 18 operates in a mannersimilar to the previously-described embodiments.

FIG. 19-20 shows a section view of another embodiment. In thisembodiment, a pump 500 comprises a piston 560 and a pumping chamber 530with an inlet 510 and outlet 520. Pumping chamber 530 further comprisesan elastic segment 531 that extends between inlet 510 and outlet 520. Apinch valve 535 acts as an isolation member and is positioned aboutelastic segment 531. In this embodiment the pinch valve comprises a pairof rollers 536 positioned opposite each other with elastic segment 531positioned in between rollers 536. Rollers 536 reside on a pair of rods537. Rods 537 are mounted inside pinch valve housing 538, which containsan actuator for actuating and holding rods 537 at precise positions.This actuator can be electromagnetic, hydraulic, mechanical, etc.

The operation of pump 500 involves the use of pinch valve 535 tosubstantially occlude the fluid flow between inlet 510 and outlet 520.Pinch valve 535 eliminates the need for the stationary piston utilizedin previously described embodiments. Use of pinch valve 535 furthereliminates the need for the extra solenoids or an extra motor which arenecessary to drive the second piston in other embodiments. In theembodiment of FIGS. 19-20, pinch valve 535 actuates elastic segment 531of pumping chamber 530 such that the elastic segment 531 can be open orclosed. When elastic segment 531 is open, drive piston 560 freely passesthrough elastic segment 531. When elastic segment 531 is closed, neitherfluid nor piston 560 can pass through elastic segment 531. Duringoperation, drive piston 560 is actuated in a clockwise fashion by eithertype of actuation means previously described (solenoids or motor) or asimilar actuation means. As drive piston 560 is actuated, pinch valve535 remains closed, clamping down on elastic segment 531 to prevent theflow of fluid through elastic segment 531. In essence, pinch valve 535acts similar to a secondary piston suspended in the isolation positiondescribed previously. As drive piston 560 is actuated, fluid enters thepump in the expanding volume created behind its lagging face and fluidexits through outlet 520 by means of the pressure created between theleading face of drive piston 560 and pinch valve 535. The only timeelastic segment 531 is actuated to open is at the completion of thedrive phase when drive piston 560 passes through elastic segment 531. Atall other times elastic segment 531 is pinched shut, so as to act as avalve prohibiting the flow of fluid through the segment. During thetransitional phase pinch valve 531 is directed by the control system(not shown) to open. A sensor array similar to previously describedembodiments is used to detect the position of the drive piston andsignal when it is appropriate to open pinch valve 535. A driver circuit(not shown) then delivers current to a set of solenoids (also not shown)within pinch valve housing 538 which exert a force on rods 537 of pinchvalve 535 such that they are pulled away from each other, thus openingelastic segment 531. In this embodiment, rods 537 areelectromagnetically actuated, but it should be appreciated that theycould also be mechanically or hydraulically actuated to cause theelastic segment 531 to expand and collapse (i.e., open and close). Itshould be further appreciated that elastic segment 531 is easilydeformed by external forces and can be quickly pinched shut so thatfluid is substantially occluded through arc segment 531. The elasticmaterial is also sufficiently elastic to expand back into its originalshape if external forces are removed. It should also be appreciated thatan elastic polymer is used as the arc segment that will not deteriorateor fatigue from prolonged deformation cycles. After drive piston 260passes through elastic segment, 531 the microprocessor (not shown)directs the drive system to actuate pinch valve 535 to close. Afterpinch valve 535 closes, the system is ready to perform another pumpingstroke. In this fashion, pumping strokes are repetitively performed toachieve the pumping of fluid.

Referring now to FIGS. 21-23, an embodiment comprises a pump 600 with apumping chamber 630 having an inlet 610 and an outlet 620. Pump 600further comprises a drive piston 660 and an isolation member orisolation sleeve 670 that is hollow and curved in shape. FIGS. 21 and 22show pump 600 from a top view, while FIG. 23 displays pump 600 from aside view. As shown in FIGS. 21 and 22, fluid enters pump 600orthogonally to the plane of rotation of isolation sleeve 670, throughinlet 110 pointing into the page. When drive piston 660 is detected, theisolation sleeve 670 is electromagnetically actuated to recess into theoutlet 620 to allow piston 660 to pass, as shown in FIG. 22. Actuationis achieved by electromagnets, which are positioned external to thetorus or pumping chamber 630 and generate a force on magnetic materialimbedded within isolation sleeve 670. Once piston 660 passes, isolationsleeve 670 returns to the configuration shown in FIG. 21. Pump 600 isconfigured so that the structure of pumping chamber 630 and isolationsleeve 670 bear the load created by the fluid pressure differentialacross valve sleeve 670. By utilizing the pump's structure to bear thestatic load, pump 600 does not require electromagnetic energy tomaintain isolation sleeve 670 is a fixed position.

Another embodiment is shown in FIGS. 24-25 comprising a pump 700 with apumping chamber 730, a recess 735, an inlet 710, and an outlet 720. Pump700 further comprises a piston 760 and an isolation piston 770. Pump 700operates in a manner similar to the embodiment of FIGS. 21-23 by movingisolation piston 770 into recess 735. However, unlike isolation sleeve670 of the embodiment in FIGS. 21-23, isolation piston 770 is solidrather than hollow isolation piston 770 can then rotate completelyaround recess 735 to flush out any fluid that stagnates during thepumping cycle.

Another embodiment of an isolation mechanism is shown in FIG. 26. Inthis embodiment, a portion of a pumping chamber 830 is shown in fluidcommunication with a pump outlet 820. A drive piston 860 is propelledwithin pumping chamber 830 in a manner provided for in previousembodiments, such as solenoids or electric motors. In addition, a hollowisolation piston 870 is located in outlet 820. As drive piston 860approaches outlet 820, hollow isolation piston 870 is retracted furtherinto outlet 820 and away from pumping chamber 830. This allows drivepiston to continue through pumping chamber 830 and begin a new pumpingcycle. When hollow isolation piston 870 is in the position shown at thefar left of FIG. 26, it allows fluid to exit outlet 820, but preventsfluid from bypassing outlet 820 and back flowing through an inlet (notshown, but connected to pumping chamber 830 downstream of outlet 820 sothat drive piston 860 first passes by outlet 820 and then the inlet). Inthis manner, hollow isolation piston 870 functions similar to theocclusion devices described in the discussion of previous embodiments.In the embodiment shown, hollow isolation piston 870 is retracted intooutlet 820 by the use of electromagnetic force. In other embodiments,the leading face of drive piston 860 can be tapered so that it engagesthe tapered end of hollow isolation piston 870 and forces hollowisolation piston 870 to recess into outlet 820.

Another embodiment is shown in FIGS. 27-28. In this embodiment, a pump900 comprises a pumping chamber 930, an inlet 910, an outlet 920, adrive piston 960, and an occlusion or isolation piston 970. The generalprinciples of operation for pump 900 are similar to those of thepreviously described embodiments. However, in this embodiment, occlusionpiston 970 comprises a slot 971 that engages a projection 972. Theengagement of projection 972 and slot 971 provides for a structural loadbearing mechanism to hold occlusion piston in place during the drivecycle of pump 900. As drive piston 960 approaches occlusion piston 970,occlusion piston 970 is withdrawn via electromagnetic or other suitableforce, to allow drive piston 960 to pass.

Another embodiment is shown in FIGS. 29-30. In this embodiment, a pump1000 comprises an inlet 1010, an outlet 1020, a pumping chamber 1030, adrive piston 1060, and an isolation piston 1070. Pump 1000 operates inthe same general manner as previously described embodiments, butincorporates isolation piston 1070 that has an upper hollow portion 1071and a solid lower foot 1072. With this configuration, isolation pistonallows fluid to enter pumping chamber 1030 when it is in the positionshown in FIG. 29. In addition, solid lower portion 1072 seals off inlet1110 when isolation piston 1070 is in the position shown in FIG. 30,thereby reducing backflow.

One advantage of recessing valve embodiments, such as those shown inFIGS. 21-29 is that each piston can be specifically designed for asingle function instead of each piston having to take turns being eitherthe drive piston or the isolation piston, thus sharing functions. Byallowing for each piston to have a separate and individual function,each piston can be optimized to perform its function without makingdesign concessions needed for the piston to serve both the drive andisolation functions. Specifically, the isolation piston can be designedto bear hydrostatic and dynamic fluid loads structurally to minimize thepower consumed to occlude fluid flow. The isolation piston can also beshaped to provide smooth inflow and outflow fluid transition. The drivepiston, relieved of its duty to act as an isolation piston every othercycle, can be optimized for a more continuous actuation cycle, low drag,and stability. The actuation and valving power can also be significantlyreduced as compared to designs that require the control system to holdthe isolation piston in place.

Another embodiment of the present invention utilizes raised or groovedsections of the torus and/or pistons to control the position and thepoints where the piston contacts the inner torus wall. Referring now toFIG. 31, a piston 1100 comprise four raised ridges 1101. Ridges 1101provide contact points with the torus wall (not shown in FIG. 31) thatcan be employed to minimize the contact area, decrease shearingstresses, decrease stagnation points, provide a controllable pistonposition, control the wear of the contact surface, and provide alubricious sliding surface. Raised ridges 1101 may be comprised of adifferent material than the rest of piston 1100 and can be made of aceramic or ultrahigh density polymer for favorable long term wear andlubricity characteristics.

Referring now to FIG. 32, another embodiment comprises ridges 1151employed along an inner wall 1152 of a torus 1150. Ridges 1151 aresimilar to ridges 1101 in the previously described embodiment.

Additional embodiments shown in FIG. 33 show four configurations forpiston wall contact ridges in cross section. In addition to theembodiments previously described in FIGS. 31 and 32, an embodimentcomprises a torus 1160 that utilizes raised portions 1161 to createcircumferential grooves 1163. In this embodiment, piston 1165 has ridges1164 that engage grooves 1163.

Yet another embodiment comprises a piston 1170 with grooves 1171 and atorus 1175 with grooves 1176. This embodiment also includes ballbearings 1177 engaged with grooves 1171 and 1176, which provides a lowfriction surface contact.

Referring now to FIGS. 34A-34D, another embodiment of the presentinvention comprises a pump 1200 for the circulation of two independentcircuits of fluid. In the embodiment shown, a toroidal pumping chamber1250 contains three pistons 1210, 1211 and 1212 and has two inlet ports1240, 1260 and two outlet ports 1270, 1280. The three pistons 1210-1212are comprised of a magnetic material and can be actuated by a variety ofmeans, including those previously described, such as a motor orelectromagnets. The pumping of both chambers of fluid is performed infour steps. In the first step Piston 1212 is in a position 1 where itoccludes fluid flowing through outlet port 1240. Piston 1210 is inposition 2 and occludes fluid from flowing through inlet port 1240.Piston 1211 is positioned by electromagnets or other means (not shown)to reside in position 4 where it occludes fluid from flowing throughinlet port 1240. The first bolus is pumped, as seen in the FIG. 34A bythe actuation of piston 1210 from position 2 to position 3. During thisactuation, fluid enters the chamber through inlet port 1240 and exitsthe chamber through port 1270, effectively pumping the chamber volumethrough port 1270 and refilling the chamber volume through port 1240. Asseen in FIG. 34B, the next step, a transitional step, is performed byactuating piston 1212 to move from position 1 to position 2. In thisposition it now occludes inlet port 1240 and has opened outlet port 1280for fluid transport. As seen now in FIG. 34C the third step in thepumping cycle is performed. In this step, the second chamber is pumpedby the actuation of piston 31211 from position 4 to position 1. Duringthis actuation the second chamber of fluid exits port 1280 and fluidrefills the chamber behind piston 1212 by entering through port 4.Piston 1211 ends its actuation stroke at position 1 where it occludesport 1280. A second transitional step in FIG. 34D is then performed byactuating piston 1210 from position 3 into position 4 so that itoccludes inlet port 1240. At the end of this transitional step, the pumphas returned to its original state and is ready to perform the previousfour steps again. In this way, two independent chambers of fluid may bepumped.

The embodiment shown in FIG. 35 pertains to the use of a pacemaker 1310connected to a pumping system 1399 in the application of ventricularassistance or biventricular cardiac pumping support. Many patients whosuffer from congestive heart failure require ventricular assistance inthe presence of a pacemaker. The embodiment of FIG. 35 illustrates asystem that employs both a pump 1300 and the pacemaker 1310 that cancontrol both the timing of the pump ejection and the timing of cardiaccontraction. In this way the pump ejection can be timed to coincide withany particular part of the cardiac cycle. This is advantageous becausesynchronicity of pump ejection can greatly decrease the cardiac workloadand can lead to healing of the damaged myocardium. A pacemaker isconnected to a single or plurality of depolarizing electrodes 1320 thatare inserted or attached to the native heart 1330. The pacemakergenerates a depolarizing electric field at the electrode tip (not shown)that creates a depolarization of the myocardium resulting incontraction. The pacemaker generates these depolarizing stimuli at aperiodicity that can be fixed or controlled either by pacemaker 1310itself or by a microprocessor 1340 of pump system 1399. Pacemaker 1310is electrically connected to microprocessor 1340 and information canflow freely between them. Microprocessor 1340 can direct pacemaker 1310to change its periodicity of heart stimulation by means of a controlsignal. Likewise, the pacemaker can direct the microprocessor to causethe pump to eject by means of a control signal. Microprocessor 1310 iselectrically connected to a control circuit or driver circuit 1350 whichis connected to pump 1300. Pump 1300 is outfitted with one or moresensors 1360 which feedback position information to control circuit 1350and which allows for proper actuation of the internal pistons (notshown) of pump 1300. Physiological sensing electrodes 1370 are connectedto the patient's body 1380 and can be employed to measure changes inneeded circulatory demand as the patient's activity level is changed.These physiological sensing electrodes 1370 can be made to measure avariety of metrics that indicate the need to increase or decrease heartrate such as the thoracic impedance, renal sympathetic nerve activity,aortic nerve activity, p-wave of the heart, acceleration of the body, orlactic acid levels. Upon receiving an input from physiological sensingelectrodes 1370, pacemaker 1310 may increase or decrease its frequencyof depolarization. This information may be relayed to microprocessor1340 which could increase the rate at which the pump executes itspumping stroke in order to stay in sync with native heart 1330.Pacemaker 1310 can possess its own internal power supply such as a smallbattery (not shown) or can be powered by means of the same supply thatdrives the operation of pump 1300. Microprocessor 1340 is connected to apower supply 1390 which powers its internal circuits as well as directspower to pump 1300 when in operation.

Referring now to FIG. 36, a side section view illustrates one embodimentof a piston 1400 disposed within a pumping chamber 1430. In certainembodiments pumping chamber 1430 is configured as a torus (or any othercontinuous ring or loop). However, piston 1400 may be incorporated intoany of the exemplary embodiments of pumps disclosed herein. In theembodiment shown, pumping chamber 1475 comprises an inner perimeter 1459having an upper chamber wall 1445, a lower chamber wall 1455, an innerchamber wall 1460 and an outer chamber wall 1465. In the view shown inFIG. 36, piston 1400 is moving to the left within pumping chamber 1475,while in FIG. 37 piston 1400 is moving toward the viewer. Pumpingchamber 1430 is centered on a central axis 1471, as shown in FIG. 37.FIG. 38 represents a top view of piston 1400, which is traveling up inthis view. Piston 1400 comprises an inner surface 1420, an outer surface1425, an upper surface 1431, a lower surface 1435, a leading face 1426and a trailing face 1421. It is understood that the terms “upper”,“lower”, “inner” and “outer” are used herein as labels for convenienceas shown in figures and not necessarily indicative of position duringactual use. In general, inner surface 1420 is closer to central axis1471 than is outer surface 1475. The terms “leading” and “trailing” areused to indicate the surfaces facing toward and away from the directionof piston travel, respectively. Upper surface 1431 and lower surface1435 are adjacent to both leading and trailing faces 1426 and 1421 aswell as inner and outer surfaces 1420 and 1425. In the embodiment shown,upper surface 1431 is proximal to upper chamber wall 1445, lower surface1435 is proximal to lower chamber wall 1455, inner surface 1420 isproximal to inner chamber wall 1460, and outer surface 1425 is proximalto outer chamber wall 1465. Piston 1400 is magnetically coupled to uppermagnetic linkage 1440 through upper torus wall 1445 and to lowermagnetic linkage 1450 through lower chamber wall 1455.

In exemplary embodiments, one or more of inner surface 1420, outersurface 1425, upper surface 1431, and lower surface 1435 comprise ahydrodynamic bearing surface. In addition, a piston surface may comprisea hydrodynamic bearing surface which resists displacement in more thanone axis. For example, as shown in the embodiment of FIGS. 36-38, uppersurface 1431 and lower surface 1435 act as hydrodynamic bearings. In theprimary direction of travel for piston 1400 (i.e., around pumpingchamber 1475), hydrodynamic forces arise from the top and bottomsurfaces which act to resist displacement of the piston towards theouter chamber wall as well as towards the upper and lower chamber walls.

Hydrodynamic bearing surfaces are incorporated on piston 1400 in orderto offset forces (such as gravity, magnetic, and centrifugal forces)that would tend to bring piston 1400 into contact with pumping chamber1475. By reducing the likelihood of contact between the piston and thechamber walls, shearing stresses can be greatly reduced and mechanicalwear to the pistons and chamber walls can be prevented. Hydrodynamicbearing surfaces create “lift” (i.e. a force directing piston 1400 awayfrom a stationary surface in a direction normal to the bearing surface)as piston 1400 moves within pumping chamber 1475. The hydrodynamicsurfaces create lift by allowing a portion of fluid within pumpingchamber 1475 to backflow across a surface of piston 1400 as it travelsthrough the fluid and within pumping chamber 1475.

As shown in FIG. 36, upper and lower surfaces 1430 and 1435 are slightlyangled so that the distance between upper surface 1435 and upper chamberwall 1445 decreases between leading face 1426 and trailing face 1421. Itis understood that the Figures are not to scale, and that the angles ofcertain surfaces may be exaggerated to provide clarity. The distancebetween lower surface 1435 and lower chamber wall 1455 also decreasesbetween leading face 1426 and trailing face 1421. As a result, thethickness of a fluid film between piston 1400 and lower chamber wall1455 changes from a maximum lower film thickness 1481 to a minimum lowerfilm thickness 1482. Under conservation of mass principles, withrelative motion between lower surface 1435 and lower chamber wall 1455,the fluid between piston 1400 and lower chamber wall 1455 can create ahydrodynamic force (represented by arrow 1485) that acts on piston 1400and directs it away from lower chamber wall 1455. As a result, frictionor drag forces between piston 1400 and lower chamber wall 1455 andshearing stresses in the respective film layer are reduced. In certainembodiments, upper surface 1431 may also comprise a hydrodynamic bearingsurface to produce a force directing piston 1400 away from upper chamberwall 1445. In this manner, upper and lower surfaces 1430, 1435 may be“tuned” so that piston 1400 should not contact either upper or lowerchamber wall 1445, 1455 during normal operation. In still otherembodiments, it may be possible to eliminate the hydrodynamic bearingsurface on upper surface 1435 and allow gravity or magnetic link forcesto repel upper surface 1435 from upper chamber wall 1445. However,because the ultimate orientation of a pump incorporating piston 1400 maynot be known, it may be necessary to provide hydrodynamic bearingsurfaces on both upper and lower surfaces 1430 and 1435.

Referring now to FIG. 38, a top view illustrates that leading face 1426may be smaller than trailing face 1421. As a result, the distancebetween outer surface 1425 and outer chamber wall 1465 decreases from amaximum film thickness 1483 at leading face 1426 to a minimum filmthickness 1484 at trailing face 1421. Under the same principlesdiscussed in the description of FIG. 36, a hydrodynamic force(represented by arrow 1486) can be created to act on piston 1400 anddirect it away from outer chamber wall 1465. Hydrodynamic force 1486 maybe used to counteract the centrifugal force or magnetic link forcescreated during normal operation that tends to direct piston 1400 towardsouter chamber wall 1465.

In addition, the gap between inner surface 1421 and inner chamber wall1460 also may decrease between leading face 1426 and trailing face 1421to create a hydrodynamic force to direct piston 1400 away from innerchamber wall 1460. However, because centrifugal force or magnetic linkforces will direct piston 1400 away from inner chamber wall 1460 duringoperation (regardless of the orientation of the pump), it may not benecessary to include a hydrodynamic bearing surface on inner surface1420.

Referring now to FIG. 37, an end section view of piston 1400 withinpumping chamber 1475 is shown. As shown in this embodiment, uppersurface 1431, lower surface 1435, upper chamber wall 1445 and lowerchamber wall 1455 are not perpendicular to a plane that extends throughcentral axis 1471 perpendicular to the page. Upper surface 1431, lowersurface 1435, upper chamber wall 1445 and lower chamber wall 1455 arealso angled relative to a plane extending through lateral axis 1472perpendicular to the page. Therefore, as piston 1400 moves towards outerchamber wall 1465 (e.g., due to centrifugal force), an upper gap 1487between upper surface 1431 and upper chamber wall 1445 (and a lower gap1488 between lower surface 1435 and lower chamber wall 1455) willdecrease. As the upper and lower gaps 1487, 1488 decrease, the pressureon a fluid between piston 1400 and upper and lower chamber walls 1445,1455 will increase. As a result, a pair of forces (represented by arrows1491 and 1492) acting on piston 1400 will be generated. Forces 1491 and1491 each have a component that resists displacement of the piston 1400towards outer wall 1465 and a component that resists displacement ofpiston 1400 towards the upper 1445 or lower 1455 chamber walls duringoperation.

While piston 1400 is illustrated in this embodiment with hydrodynamicbearing surfaces on upper surface 1431, lower surface 1435, innersurface 1420, and outer surface 1425, it is understood that otherembodiments may comprise a piston with hydrodynamic bearing surfaces onfewer surfaces. For example, the hydrodynamic bearing surfaces may beeliminated on inner surface 1420 and outer surface 1425. In suchembodiments, upper surface 1431 and lower surface 1435 may be configuredas shown in FIGS. 36 and 37 to provide stabilization forces bothlaterally and vertically. As discussed in the description of FIG. 37,upper and lower surfaces 1430 and 1435 can be configured to generateforces 1491 and 1492 to balance the centrifugal and magnetic forces andtherefore provide lateral stabilization. As a result it may not benecessary to provide hydrodynamic bearing surfaces on inner surface andouter surfaces 1420 and 1425. However, it may be desirable to providehydrodynamic bearing surface on inner and outer surfaces 1420 and 1425to provide additional forces directing piston 1400 away from inner wall1421 and outer wall 1425. It should be understood that passivelevitation of piston 1400 while it is moving can be achieved through useof hydrodynamic surfaces in this manner. Displacement of piston 1400from its levitating position will increase hydrodynamic forces which actto resist the displacement and restore piston 1400 back to itslevitating equilibrium position.

While exact dimensions will depend on numerous factors (such as theoverall piston size and configuration, the fluid properties, etc.) incertain embodiments the minimum film thickness is approximately0.00025-0.001 inches and the maximum film thickness is approximately0.003-0.004 inches. Other factors, such as surface finish, may alsoaffect the ability to generate hydrodynamic forces. In certainembodiments, the surface finish of piston 1400 and the interior walls ofpumping chamber 1475 is between 1 and 16 microinches (as defined by thecenterline average surface finish R_(a)).

It is also understood that in certain embodiments a piston may comprisea cross-section different than piston 1400 shown in FIG. 37. Examples ofvarious end views of exemplary pistons are provided in FIGS. 39-42A. Asshown in FIG. 39, piston 1401 comprises an upper surface portion 1407that is not perpendicular to axis 1471 and is angled down towards alower surface portion 1408 (which is also not perpendicular to axis 1471and is angled up towards upper portion 1407). Similarly, piston 1402shown in FIG. 40 comprises an upper surface portion 1417 that is notperpendicular to axis 1471 and is angled down towards lower surfaceportion 1418 (which is not perpendicular to axis 1471 and is angled uptowards upper surface portion 1417). As shown in FIG. 41, piston 1403comprises an upper surface portion 1427 that is not perpendicular toaxis 1471 and is angled down towards a lower surface portion 1428 (whichis also not perpendicular to axis 1471 and is angled up towards upperportion 1427). In other embodiments, a piston may have a cross-sectionin which the entire upper or lower surfaces are perpendicular to thecentral axis of the pumping chamber. One example is shown in FIG. 42A,in which piston 1404 comprises a rectangular cross-section. Similar tothe description of FIGS. 36-38, displacement of a piston 1401, 1402,1403 or 1404 in any direction which results in a decrease in thedistance between a piston surface and a chamber wall gives rise tohydrodynamic forces which resist this displacement and acts to restorethe piston back to the equilibrium position. By reducing the likelihoodof contact between the piston and the chamber walls, shearing stressesin the fluid are minimized.

Referring now to FIG. 42B, detailed views of exemplary embodiments ofhydrodynamic bearing surfaces are shown to comprise various differentshapes. In the embodiments shown, a plurality of pistons 1801-1808comprise a hydrodynamic bearing surface 1811-1818 proximal to astationary surface 1850 (such as an inner surface of a pumping chamber).A first embodiment shows piston 1801 with hydrodynamic bearing surface1811 comprising a tapered surface 1821 across piston 1801. In a secondembodiment, piston 1802 comprises a hydrodynamic bearing surface 1812that forms a convex curved surface 1822 across piston 1802. As shown, athird embodiment comprises piston 1803 with hydrodynamic bearing surface1813 forming a concave curve surface 1823 across piston 1803. Referringnow to piston 1804, hydrodynamic bearing surface 1814 comprises a singlestep 1824 proximal to stationary surface 1850. As shown on piston 1805,hydrodynamic bearing surface 1815 comprises an angled surface 1825 thatextends partially across piston 1805. Piston 1806 comprises ahydrodynamic bearing surface 1816 that includes an angled surface 1826and a step 1836. As shown on piston 1807, hydrodynamic bearing surface1817 includes two separate angled surfaces 1827, 1837 with angledsurface 1827 extending part of the way across piston 1807 and angledsurface 1837 extending part of the way across piston 1807. Referring nowto piston 1808, hydrodynamic bearing surface 1818 comprises a first step1828 and a second step 1838. It is understood that each of the shapesshown in hydrodynamic bearing surfaces 1801-1808 are merely examples ofa multitude of different configurations that can be used to createhydrodynamic bearing surfaces. A hydrodynamic bearing may comprise anysurface configured to create “lift” by allowing fluid backflow betweenstationary and moving surfaces that are proximal to each other. Backflowoccurs when a portion of the fluid moves against the predominantdirection of fluid flow (e.g., in a direction from the trailing facetowards the leading face.) Furthermore, exemplary embodiments maycomprise hydrodynamic bearing surfaces on stationary components.Referring now to FIG. 42C, one exemplary embodiment comprises a piston1900 disposed within a pumping chamber 1930 comprising an inner wall1960 and an outer wall 1965. In the embodiment shown, piston 1900comprises a leading face 1926 and a trailing face 1921, as piston 1900moves toward the right. Inner wall 1960 comprises a plurality of taperedsurfaces 1961 that act as hydrodynamic bearing surfaces when piston 1900moves relative to tapered surfaces 1961. Similarly, outer wall 1965comprises a plurality of tapered surfaces 1966 that act as hydrodynamicbearing surfaces when piston 1900 moves relative to tapered surfaces1966. In this embodiment, the same principles of operation used tocreate “lift” apply as those described in embodiments with hydrodynamicbearing surfaces placed on moving components. It is understood thatwhile inner wall 1960 and outer wall 1965 are shown to comprise angledsurfaces, other embodiments may comprise different configurations (forexample, similar to those described in FIG. 42B).

Referring now to FIGS. 43-48, another embodiment of a pumping systemcomprises a pair of motors 1545 and 1546 driving a pump 1500. Motors1545 and 1546 are generally equivalent in design, and therefore onlymotor 1545 (shown in exploded view) will be discussed in detail. It isunderstood that motor 1546 comprises features equivalent to thosediscussed regarding motor 1545. Pump 1500 comprises a pumping chamber1530 and a pair of pistons 1560, 1570. Pumping chamber 1530 comprises aremovable cap 1531 to allow for pistons 1560, 1570 to be loaded into thepumping chamber. In this embodiment, motor 1545 comprises a rotor 1544with a linking arm 1547 having extensions 1571 and arm magnets 1572 thatare disposed on either side of piston 1560 (which comprises a casing1561 and piston magnets 1562). Pump 1500 also comprises a plurality ofrotor magnets 1548, a set of coils 1549, and a stator plate 1551. Motor1545 further comprises a shaft 1556 and a bearing 1557. While FIG. 43represents an exploded view of motor 1545, FIG. 44 represents anassembled view of motor 1546.

In this embodiment, motor 1545 is an axial flux gap motor which providesfor more precise control as compared to other motor configurations. Asshown in FIG. 45, there is an axial gap between coils 1549 and rotormagnets 1548. As shown in the detail views in FIGS. 46 and 47, a magnet1566 can be coupled to the end of shaft 1556 to provide a signal thatallows for the rotational position of rotor 1544 to be determined.Specifically, magnet 1566 creates a magnetization vector 1569 that willrotate with the position of the rotor 1544. In the embodiment shown inFIG. 47, a sensor 1567 (such as a 2-axis Hall effect sensor) is coupledto a printed circuit board 1568, which is coupled to a microprocessor(not shown).

FIG. 48 provides a flowchart illustrating the basic steps in oneembodiment of a control system 1590 that can be used to control motor1545. Other embodiments may use different control systems. In summary,the microprocessor takes information from sensor 1567, conditions it,interprets it to an angular position, compares it with a desired angularposition to get an error signal, multiplies this error signal by a gain,translates the control signal to a pulse width modulated signal, andthen applies this to the correct phases of motor 1545 via a commutationsequence.

In step 1591, the microprocessor receives two lines of information fromeach motor 1545, 1546, which are output from sensor 1567 (and the sensorfor motor 1546). For purposes of clarity, only the control system formotor 1545 will be discussed in detail. It is understood that thecontrol of motor 1546 operates under the same general principles. Thisinformation contains the Cartesian components of the net magnetizationvector 1569 that exists over sensor 1567, which is directly produced bymagnet 1566. When rotor 1544 and shaft 1556 rotate, so does magnet 1566.As a result, the magnetization vector 1569 rotates proximal to sensor1567. As magnet 1566 rotates, the magnitude and direction of the x and ycomponents change according to tan(theta)=y/x, where theta is theangular position of the magnetization vector 1569 in the plane parallelto the sensing plane of sensor 1567. Thus, contained in the x and ysignal lines lies the information to deduce the angular position ofrotor 1544.

The x and y signals enter the microprocessor via data acquisitionhardware (not shown) that samples at a frequency (e.g. 250 kHz)sufficient to detect rapid changes in the position of rotor 1544. Incertain embodiments, the samples are conditioned in step 1592 via a4^(th) order Butterworth filter to remove high frequency noise. Thisconditioned x and y data are then passed to the next operation in step1593.

The Look up Angular Position loop in step 1593 (operating at 1microsecond per loop iteration in certain embodiments) takes theconditioned x and y data and, using comparison operations, selects oneof four lookup tables to determine the theta position of rotor 1544based on the x and y data. The loop first determines which variable (xor y) is most sensitive at that given point in time by comparing thevalues of x and y to a predetermine table. After it has been determinedwhich variable is more sensitive, one of four lookup tables, which havebeen pre-calibrated with the x and y variable data for each ¼ degreeangular position of the rotor to determine the rotor's position within ¼of a degree for that point in time. The angular position is output inbits, each of which correspond to 0.25 degrees in certain embodiments.

Once the theta position of rotor 1544 has been determined, thisinformation passes to two separate operation loops. The Tracking Controlloop in step 1594 (executing at a speed controlled by the user,typically 0.1-10 msec per loop iteration) looks at the current angularposition of rotor 1544. It then compares this to a desired position forrotor 1544 for that particular point in time and calculates the error bytaking the difference. In certain embodiments, the Tracking Control loopin step 1594 has its own clock that starts at zero and steps throughconsecutive values at the loop rate specified by the user. A look-uptable containing the desired position of rotor 1544 as a function oftime takes the present clock value and returns the desired rotorposition for that time. The desired position is then compared to theactual position of rotor 1544 and an error is computed. As the TrackingControl loop in step 1594 cycles, the clock increments and returns thenext desired theta value from the lookup table. In this way, a desiredposition versus time profile for rotor 1544 to follow can beimplemented. The internal clock of this loop is reset by a trigger thatis activated when the position of second piston 1570 crosses a certainthreshold. The output from this loop is the difference between the rotorposition and the desired rotor position. This error signal is then sentto the PID Controller.

The PID Controller in step 1595 takes the error signal and computes again by multiplying the error, the integral of the error, and thederivative of the error by a proportional gain variable, integral gainvariable, and derivative gain variable respectively. The values of thesethree variables are specified and tuned by the user. The PID controllerin step 1595 then sums these errors and outputs an overall Gain whichwill be used to tell the rotor of the motor which direction to move andhow strongly to move in this direction. This particular PID controller1595 also uses anti-windup capability which allows for the integral gainto be reset to zero on certain events. This is used to prevent largeovershoots of the desired position when rotor 1544 is told to stop at acertain position.

The gain from the PID Controller in step 1595 and the angular positioninformation from the Look-up Angular Position loop in step 1593 are thenprocessed by the Commutator/PWM Output loop in step 1596. In certainembodiments, this loop executes in 25 nanoseconds. This loop performstwo operations and outputs the information to control the driver circuit1597 which ultimately controls the magnitude and direction of thecurrent that is applied to each phase of motor 1545. The Commutatorportion of loop 1596 uses the current angular position of rotor 1544 todetermine which phases to activate in order to actuate rotor 1544. Incertain embodiments, motor 1545 is a brushless DC motor with six polepairs and nine coils. This yields six symmetric configurations of therotor and coils. For each of these six repeating sequences there are sixcommutation steps. This design follows a basic six-step commutationscheme for brushless DC motors. In certain embodiments, this scheme isas follows: 1 0 −1: phase 1 FWD, phase 2 OFF, phase 3 REV.

-   -   1 −1 0: phase 1 FWD, phase 2 REV, phase 3 OFF    -   0 −1 1: phase 1 OFF, phase 2 REV, phase 3 FWD    -   −1 0 1: phase 1 REV, phase 2 OFF, phase 3 FWD    -   −1 1 0: phase 1 REV, phase 2 FWD, phase 3 OFF

Where FWD refers to applying a forward bias drive voltage to the phase,REV refers to applying a reverse bias drive voltage to the phase, andOFF refers to applying no voltage to the phase.

By stepping through each of these configurations in a certain order,rotor 1544 can be made to rotate by the magnetic fields produced by thephases. Thus in order to achieve a single 360 degree rotation of motor1545, this six step commutation sequence must be stepped through sixtimes for a total of 36 steps per rotation. Stepping through each of the36 phase configurations is performed by the Commutator loop in step 1596by comparing the current angular position of rotor 1544 to an arraywhich tells which of the six steps to use for a particular range inangular position values. For instance, when rotor 1544 is between zeroand ten degrees it would use one of the six commutation steps, uponcrossing into the 10 to 20 degree range, it would use the next phaseactivation configuration and so on.

The second part of the Commutation/PWM loop in step 1596 is thetranslation of the gain signal into a pulse width modulated signal forthe driver circuitry. In certain embodiments, each phase is driven by anh-bridge MOSFET that takes a single pulse width modulated input tocontrol both the magnitude and direction of the voltage applied to coils1549. In certain embodiments, when the input line to the MOSFET is at a50% duty cycle, the bias voltage across the phase coils is zero. For aPWM duty cycle of 100% (i.e. 5V DC), the coil is forward biased with thefull driving voltage (e.g. 12 V). For a PWM duty cycle of 0% (0 V DC),the phase receives the full drive voltage in the reverse bias direction.For a duty cycle of 75%, the phase receives 50% of the drive voltage inthe forward biases direction, and so on.

In certain embodiments, the algorithm in the Commutation/PWM loop instep 196 generates this signal in the following way. There is a counterin the loop that increments every tick of the 40 MHz FPGA clock (25nsec). This counter is programmed to reset every 2000 ticks (50 usec).For each phase, the loop determines how many ticks out of the 2000 tickperiod that the lines should be turned on. On the rising edge of each 50usec pulse period the angular position of the motor is used to determinethe commutation step to use (1, −1, or 0). The magnitude of the gainfrom the PID controller is then multiplied by this commutation step togenerate the on-time for that particular 50 usec pulse period. The valueof 1000 is added to the gain signal in order to account for the factthat an on-time of 1000 ticks is needed to produce zero voltage across aphase (1000/2000=50% duty cycle=0 Volts across phase). Finally, the signof the gain signal is used to determine which direction to apply thevoltage (forward or reverse bias). If the gain is negative, the PWMsignal is inverted, thus a 75% on, 25% off PWM signal to the drivercircuit which would generate a 50% forward voltage across the phase,would be switched to a 25% on, 75% off PWM signal which would create a50% reverse voltage to be applied to the phase. This is one advantage ofhaving the zero voltage of the driver existing at a duty cycle of 50%;inversion of the duty cycle reverses the direction but leaves themagnitude the same. For instance, a gain of 500 with a commutation stepof 1, −1, 0 would tell phase 1 to turn on for 1500 (500+1000) ticks ofthe 2000 tick pulse period, resulting in a duty cycle of 75% to thedriver circuit which would apply 50% of the drive voltage in the forwardposition to phase 1, 50% reverse bias for phase 2, and zero volts forphase 3. As the gain varies depending on how close the angular positionis to the tracking target angle, the PWM duty cycle varies to apply moreor less of voltage to the phases and to move the rotor in a clockwise orcounterclockwise direction to minimize said angular error. In thisfashion rotor 1544 can be controlled to follow many enteredposition-time profiles as well as stopping and holding on any particularangle.

By having a tracking controller in which rotor 1546 follows a particularpath as it cycles, the position of the piston 1560 can be actuated togenerate a variety of hydraulic output profiles. Such profiles may beused in applications requiring pulsatility. The position and velocity ofthe piston may also be controlled to produce a predetermined waveform inthe outlet flow of fluid from the pump.

Referring now to FIGS. 49-51, another embodiment of a pump 1600comprises a lower casing 1610, an upper casing 1620, a pumping chamber1630, an inlet conduit 1640, and inlet port 1641 and an outlet 1650.Pump 1600 further comprises a pair of pistons 1660, 1670 driven by amotor 1645, which comprises a rotor 1625, a bearing 1657, a set of coils1649, and magnets 1648. Pump 1600 also comprises a magnetic ring 1655and an electromagnet 1615. It is understood that magnetic ring 1655 maynot form a complete circle; for example, magnetic ring 1655 may comprisea gap 1653 in which electromagnet 1615 is positioned. Similar topreviously-described embodiments, shaft 1656 may contain a magnet 1666that is detected by a sensor 1667 to determine the rotational positionof rotor 1625.

Unlike previous embodiments which require a separate motor to move eachpiston around the pumping chamber, pump 1600 moves both pistons 1660,1670 with a single motor 1645. In certain embodiments, a magnetic link1647 is coupled to a rotor 1644. Magnetic link 1647 is first coupled topiston 1660, while piston 1670 is held in place by an electromagnet1615. FIGS. 52-56 illustrate one embodiment of how magnetic link 1647transitions from being initially coupled to piston 1660 and beingsubsequently coupled to piston 1670 (while both piston 1660 and piston1670 are located in pumping chamber 1630). The labels “N” and “S” referto the north and south poles of the magnets, respectively. It is alsounderstood that while pistons 1660 and 1670 are shown with taperedsurfaces that can act as hydrodynamic bearing surfaces, otherembodiments may not include hydrodynamic bearing surfaces. Referringinitially to FIGS. 52 and 53, magnetic link 1647 is linked to piston1660 and piston 1670 is held stationary by electromagnet 1615. As rotor1625 rotates, piston 1660 is directed around pumping chamber 1630. Withpiston 1670 held in place, the movement of piston 1660 forces fluid frompumping chamber 1630 to exit through outlet 1650 (shown in FIGS. 49 and50). As shown in FIG. 54, when piston 1660 approaches piston 1670,electromagnet 1615 is momentarily turned off so that piston 1670 is nolonger held in place by electromagnet 1615. Piston 1670 is thendisplaced by piston 1660 (or fluid pressure between pistons 1660 and1670). In certain embodiments, the current applied to electromagnet 1615can be reversed to apply a repulsive force to piston 1670. As shown inFIG. 55, magnetic link 1647 then moves piston 1660 into the locationpreviously occupied by piston 1670. At this point, electromagnet 1615 isre-energized so that it holds piston 1660 in place. Referring now toFIG. 56, magnetic link 1647 then directs piston 1670 around pumpingchamber 1630 while piston 1660 is held stationary. While piston 1670travels around pumping chamber 1630, it forces fluid to exit throughoutlet 1650. As piston 1670 approaches piston 1660, electromagnetic 1615is again de-energized so that piston 1660 is no longer held in place.Piston 1670 (or fluid pressure between fluid 1660 and 1670) displacespiston 1660 from its location. Rotor 1625 and magnetic link 1647 thenmove piston 1670 into the location previously occupied by piston 1670.Electromagnet 1615 is re-energized so that it holds piston 1670 inplace. Rotor 1625 and magnetic link 1647 then direct piston 1660 aroundpumping chamber 1630 and the cycle is repeated. In this manner, themovement of both pistons 1660 and 1670 is controlled by a single motor1645.

Referring now to FIGS. 57-62, various embodiments of magnetic link 1647,piston 1660, and magnetic ring 1655 are shown. In FIG. 57, magnetic link1647 and piston 1660 are permanent magnets that are generally the samewidth. In FIG. 58, magnetic link 1647 is comprised of two permanentmagnets, with a stronger permanent magnet located under piston 1660 anda smaller magnet extending beyond the leading face 1623 of piston 1660.As shown in FIG. 59, magnetic link 1647 comprises a permanent magnetwith a constant thickness that extends beyond the leading face 1623 ofpiston 1660. Referring now to FIG. 60, magnetic link 1647 comprises apermanent magnet that extends beyond the leading face 1623 of piston1660 and tapers to a thinner cross-section. In the embodiment of FIG.61, piston 1660 and magnetic link 1647 also each comprise a Halbacharray. In the embodiment shown in FIG. 62, piston 1660 and magnetic link1647 each comprise a Halbach array. In addition, magnetic link 1647further comprises an extension of magnetically permeable material 1646.The inclusion of an extension of magnetic link 1647 past the leadingface 1623 of piston 1660 may provide for a smoother transition frompiston 1660 to piston 1670.

Because magnetic link 1647 acts on only one side of pistons 1660, 1670the forces on piston 1600 may not be balanced. Pistons 1660 and 1670 cantherefore experience increased drag or friction forces against theportion of pumping chamber 1630 that is proximal to magnetic link 1647.To counteract this force, certain embodiments of pump 1600 comprisemagnetic ring 1655 positioned so that pistons 1660, 1670 are locatedbetween magnetic link 1647 and magnetic ring 1655. As shown in thedetail view of FIG. 51, magnetic ring 1655 can be positioned so that itis generally parallel with rotor 1625. Therefore, magnetic ring 1655 canoffset the magnetic forces exerted on pistons 1660, 1670 by magneticlink 1647 and reduce the drag or friction forces created when pistons1660, 1670 move within pumping chamber 1630. In other embodiments, otherfeatures may be used to offset the magnetic forces acting on pistons1660, 1670, and a magnetic ring may not be used. For example, pistons1660, 1670 may incorporate a hydrodynamic bearing surface that creates aforce opposing the magnetic force provided by magnetic link 1647.Additionally, magnetic ring 1655 can be used in combination withhydrodynamic bearing surfaces to enable passive levitation of the pistonas it moves within the chamber.

Referring now to FIG. 63, a detailed view of one embodiment of magneticring 1655, piston 1660, magnetic link 1647 and rotor 1625 illustrateshow Halbach arrays may be incorporated to reduce the required magnetsize and/or increase the magnetic forces created. As understood by thoseskilled in the art, a Halbach array is an arrangement of magnets whichincrease the magnetic field on one side of the array, and reduces themagnetic field on the opposing side. Additionally, the Halbach array canbe used to prohibit excessive drifting of piston 1660 relative magneticlink 1647 when forces arise to displace piston 1660 from magnetic link1647. In the embodiment shown in FIG. 63, magnetic ring 1655 comprises aHalbach array configured to increase the magnetic field on the sideclosest to piston 1660. In addition, piston 1660 comprises two Halbacharrays (which may be joined with epoxy or any other suitable means)configured to increase the magnetic field on the side closest tomagnetic ring 1655. In addition, magnetic link 1647 comprises a Halbacharray configured to increase the magnetic field on the side closest topiston 1660. It is understood that FIG. 63 is just one exemplaryembodiment, and that other embodiments may not comprise Halbach arraysin magnetic ring 1655, piston 1660, or magnetic link 1647.

Referring back now to FIG. 50, inlet conduit 1640 is shown to extendfrom the central portion of pumping chamber 1630 rather than theperimeter. As shown in the perspective view of FIG. 64, inlet conduit1640 also extends generally perpendicular to pumping chamber 1630 andoutlet 1650. Referring now to FIGS. 65 and 66, such a configurationallows pump 1600 to be placed in the human body so that inlet conduit1640 extends into a patient's left ventricle 1683. Outlet 1650 may becoupled to ascending aorta 1684 via conduit 1685 as shown in FIG. 65.Outlet 1650 may also be coupled to descending aorta 1686 via conduit1687, as shown in FIG. 66. In certain embodiments, outlet 1650 isanastomosed to ascending aorta 1684 or descending aorta 1686.

Referring now to FIGS. 67-69, another embodiment of a pump 1700 utilizesa single motor 1745 to drive a pair of pistons 1760, 1770. However, thebasic configuration of this pump more closely resembles that of pump1500 shown in FIG. 43, rather than pump 1600 shown in FIG. 49. Morespecifically, inlet 1740 and outlet 1750 do not extend perpendicular toeach other and lie in the same plane as pumping chamber 1730. Componentsin FIG. 67 that are equivalent to components in FIG. 43 are labeled withlike numbers, with the exception that FIG. 67 components begin with“17xx” and components in FIG. 43 begin with “15xx”. In the interest ofbrevity, a full description of the components will not be repeated here.

Pump 1700 differs from pump 1500 in that pump 1700 comprises a singlemotor 1745 to control both pistons 1760 and 1770. In addition, pump 1700comprises an electromagnet 1575 comprising a permeable core 1573 and acoil 1574. Pump 1700 operates with the same general principles as thosedescribed in the discussion of pump 1600. However, pump 1700 may notrequire a magnetic ring similar to magnetic ring 1655 because armmagnets 1772 are disposed above and below pistons 1760 and 1770.Therefore, the magnetic forces acting on pistons 1760 and 1770 can bebalanced without the use of a separate magnetic ring.

It should be appreciated that the exemplary embodiments previouslydescribed can be operated in a forward direction where fluid is drawninto the pump through the inlet conduit and ejected through the outletconduit or in a reverse direction where the fluid enters the outlet andexits through the inlet conduit. Reverse operation in achieved by simplyactuating the pistons in the reverse direction.

While the above description contains many specifics, these should not beconstrued as limitations on the scope of the invention, but asexemplifications of the presently preferred embodiments thereof. Manyother modifications and variations are possible within the teachings ofthe invention such as using the pump to oscillate fluid through a flowcircuit or using the pump for the precise delivery of discrete andmetered fluid quantities to a system. Other embodiments may compriseadditional features, such as one or more sensors configured to measureproperties of the pumped fluid (e.g., temperature, pH, pressure, etc.)

Thus the scope of the invention should be determined by the appendedclaims and their legal equivalents, and not by the examples given.

REFERENCES

The following references, to the extent that they provide exemplaryprocedural or other details supplementary to those set forth herein, arespecifically incorporated herein by reference.

U.S. Pat. No. 6,576,010

U.S. Pat. No. 5,089,016

1. A system comprising: a pumping chamber forming a loop; a pump inletin fluid communication with the pumping chamber; a pump outlet in fluidcommunication with the pumping chamber; a first piston disposed withinthe pumping chamber; a second piston disposed within the pumpingchamber; an electric motor; and an electromagnet, wherein the system isconfigured such that during operation: the electromagnet is initiallycoupled to the first piston; the electric motor is initially coupled tothe second piston; the electromagnet is subsequently coupled to thesecond piston; and the electric motor is subsequently coupled to thefirst piston.
 2. The system of claim 1 wherein the system is configuredsuch that during operation: the electromagnet is coupled to either thefirst or second piston when the electromagnet is energized; and theelectromagnet is not coupled to either the first or second piston whenthe electromagnet is de-energized.
 3. The system of claim 1, furthercomprising a magnetic ring, wherein the system is configured such thatduring operation: the electric motor exerts a first magnetic force onthe first piston; the magnetic ring exerts a second magnetic force onthe first piston; and the first magnetic force opposes the secondmagnetic force.
 4. The system of claim 3 wherein the magnetic ringcomprises a permanent magnet or Halbach array.
 5. The system of claim 1,wherein the system is configured such that during operation: the motorcomprises a rotor with a magnetic link; the magnetic link is initiallycoupled to the second piston and subsequently coupled to the firstpiston.
 6. The system of claim 5, wherein the magnetic link comprises apermanent magnet or Halbach array.
 7. The system of claim 5, wherein thesystem is configured such that during operation: a portion of themagnetic link extends beyond a leading face of the piston.
 8. The systemof claim 1, wherein the first piston and the second piston each comprisea permanent magnet or Halbach array.
 9. The system of claim 1 whereinthe system is configured such that during operation: the pump inlet isinserted into a ventricle; the pump outlet is in fluid communicationwith the ascending aorta, the descending aorta, or a pulmonary artery.10. The system of claim 1 wherein the system is configured such that:the motor comprises a rotor coupled to a linking arm; the linking arm iscoupled to a first magnet, wherein the first magnet is located on afirst side of the piston during operation; the linking arm is coupled toa second magnet, wherein the second magnet is located on a second sideof the piston during operation; and the first side is opposed to thesecond side.
 11. The system of claim 1 wherein the first piston or thesecond piston comprise a hydrodynamic bearing surface.
 12. A method ofpumping a fluid, the method comprising: providing a pumping chamber,wherein the pumping chamber contains the fluid; providing a pump inletin fluid communication with the pumping chamber; providing a pump outletin fluid communication with the pumping chamber; providing a firstpiston disposed within the pumping chamber; providing a second pistondisposed within the pumping chamber; providing an electric motorcomprising a rotor; providing an electromagnet; coupling theelectromagnet to the first piston; coupling the rotor to the secondpiston; holding the first piston in a first location with theelectromagnet; rotating the rotor and moving the second piston closer tothe first piston so that a portion of the fluid is forced out of thepump outlet; de-energizing the electromagnet and uncoupling theelectromagnet from the first piston; energizing the electromagnet sothat it couples to the second piston; and coupling the rotor to thefirst piston.
 13. The method of claim 12, further comprising: rotatingthe rotor and moving the first piston closer to the second piston sothat a portion of the fluid is forced out of the pump outlet.
 14. Themethod of claim 11 wherein the first location is between the pump inletand the pump outlet.
 15. A system comprising: a pumping chambercomprising an inner surface forming a loop; a pump inlet in fluidcommunication with the pumping chamber; a pump outlet in fluidcommunication with the pumping chamber; a piston disposed within thepumping chamber; and a first electric motor magnetically coupled to thepiston, wherein: the piston comprises a hydrodynamic bearing surfaceconfigured to repel the piston away from the inner surface as the pistonmoves within the pumping chamber.
 16. The system of claim 15, wherein:the loop is centered about a central axis; the piston comprises an uppersurface, a lower surface, an inner surface, an outer surface, a leadingface, and a trailing face; and the inner surface comprises an upperwall, a lower wall, an inner wall and an outer wall.
 17. The system ofclaim 16, wherein during operation: a first lower gap exists between thelower surface and the lower wall proximal to the leading face; a secondlower gap exists between the lower surface and the lower wall proximalto the trailing face; the first lower gap is larger than the secondlower gap; a first upper gap exists between the upper surface and theupper wall proximal to the leading face; a second upper gap existsbetween the upper surface and the upper wall proximal to the trailingface; and the first upper gap is larger than the second upper gap. 18.The system of claim 16, wherein a portion of the lower surface is notperpendicular to the central axis and a portion of the upper surface isnot perpendicular to the central axis.
 19. The system of claim 16,wherein: a first outer gap exists between the outer surface and theouter wall proximal to the leading face; a second outer gap existsbetween the outer surface and the outer wall proximal to the trailingface; and the first outer gap is larger than the second outer gap. 20.The system of claim 15 further comprising a pinch valve between the pumpinlet and the pump outlet.
 21. The system of claim 15 furthercomprising: a second piston disposed within the pumping chamber; asecond electric motor coupled to the second piston, wherein: the secondpiston comprises a hydrodynamic bearing surface configured to repel thesecond piston away from the inner surface as the second piston moveswithin the pumping chamber.
 22. The system of claim 15, furthercomprising: a power supply; a driver circuit electrically coupled to theelectric motor and the power supply; a microprocessor electricallycoupled to the driver circuit; and a sensor for sensing a position ofthe piston within the pumping chamber, wherein: the driver circuit isconfigured to selectively couple the power supply to the electric motorupon receiving a control signal; the sensor is electrically connected tothe microprocessor; the microprocessor is configured to interpret theposition from the sensor; and the microprocessor is configured to outputthe control signal to the driver circuit.
 23. The system of claim 15wherein a position and a velocity of the piston are controlled toproduce a predetermined waveform in an outlet flow from the pump outlet.24. The system of claim 15 further comprising a fluid within the pumpingchamber and a sensor configured to measure a property of the fluid. 25.The system of claim 15, wherein the piston or inner surface comprise oneor more of the following: a nanoparticulate surface, a microporouscoating, or a fibrous flocking configured to facilitate endothelial orpseudoneointimal protein or cell aggregation.
 26. The system of claim15, further comprising: a pacemaker; and a microprocessor, wherein thepacemaker comprises one or more electrodes electrically coupled to aheart; the pacemaker is electrically coupled to the microprocessor; thepacemaker provides a depolarization output to the one or moreelectrodes; the heart is controlled to contract at a predetermined timerelative to an actuation stroke of the pump.
 27. The system of claim 15further comprising a sensor, wherein: the sensor is configured to sensea physiological parameter; the system is configured to increase ordecrease a volumetric flow rate from the pumping chamber based on thephysiological parameter.
 28. The system of claim 27 wherein the sensorcomprises one or more electrodes for measuring thoracic impedance,p-wave activity, renal sympathetic nerve activity, or aortic nerveactivity.
 29. The system of claim 27 wherein the sensor comprises anaccelerometer for sensing a heart contraction, a diaphragm motion, abodily inclination, or a walking pace.
 30. A pump for circulating fluidcomprising: a pumping chamber; a pump inlet in fluid communication withthe pumping chamber; a pump outlet in fluid communication with thepumping chamber; a drive piston disposed within the pumping chamber; anda hollow valve sleeve configured to recess into the pump outlet.
 31. Asystem comprising: a pumping chamber forming a loop; a pump inlet influid communication with the pumping chamber; a pump outlet in fluidcommunication with the pumping chamber; a piston disposed within thepumping chamber; an electric motor comprising a rotor coupled to ashaft; a magnet coupled to an end of the shaft; a sensor proximal to themagnet; and a control system, wherein: the electric motor ismagnetically coupled to the piston; the magnet produces a magneticvector that rotates with the rotor; the sensor is configured sense themagnetic vector; and the control system is configured to determine theangular position of the rotor.
 32. The system of claim 31, wherein thesensor is a 2-axis Hall effect sensor.
 33. The system of claim 31,wherein the electric motor is an axial flux motor.
 34. The system ofclaim 31, wherein the control system is configured to access a lookuptable.
 35. A system comprising: a pumping chamber comprising an innersurface forming a loop; a pump inlet in fluid communication with thepumping chamber; a pump outlet in fluid communication with the pumpingchamber; a first piston disposed within the pumping chamber; and aseries of electromagnets disposed around the pumping chamber, wherein:the series of electromagnets are configured to move the first pistonaround the pumping chamber; and the first piston comprises ahydrodynamic bearing surface configured to repel the first piston awayfrom the inner surface as the first piston moves within the pumpingchamber.
 36. The system of claim 35 further comprising a second pistondisposed within the pumping chamber, wherein: the series ofelectromagnets are configured to move the second piston around thepumping chamber; and the second piston comprises a hydrodynamic bearingsurface configured to repel the second piston away from the innersurface as the second piston moves within the pumping chamber.
 37. Thesystem of claim 35 further comprising a pinch valve between the pumpinlet and pump outlet.